Torque-generating steering device with load-sensing capability

Description

BACKGROUND OF THE DISCLOSURE

[0001] The present invention relates to torque-generating steering devices, and more particularly, to such devices in which a relatively low-torque input is translated into a relatively high-torque steering output, with the aid of a source of pressurized fluid.

[0002] Torque generators of the type to which the present invention relates have been in commercial use for many years, and are illustrated and described in greater detail in U.S. Patent No. Re. 25,291.

[0003] Torque generators include a valve means which is displaced from a neutral position to an operating (open) position by rotation of the steering wheel. When the valve means is open, pressurized fluid flows through the valve means and into a fluid pressure actuated displacement mechanism, such as a gerotor gear set, thereby generating a relatively high-torque steering output which is transmitted by means of an output shaft to a steering apparatus, such as the pinion gear of a rack and pinion device. Although the torque generator of the present invention may be used in various applications, it is especially advantageous (and used most commonly) in vehicle steering systems, and will be described in connection therewith.

[0004] Prior art torque generators have included valving of the open-center type, such that fluid would flow from the pump through the valving to the system reservoir whenever the torque generator is not being utilized, and the valving is in its neutral position. Although the operation of such open-center torque generators has been generally satisfactory, it has been necessary to provide a second pump in the event the vehicle includes any other hydraulic devices, beside the steering system. The provision of a second pump, and the associated plumbing and controls, on the types of vehicles which normally utilize torque generators becomes prohibitively expensive.

[0005] A steering device comprising all features contained in the preamble of claim 1 is known from US-A-4 730 544. This prior steering device is designed as a full-fluid linked steering control unit in which pressurized fluid is ported to one end of the cylinder of a hydraulic steering motor having a piston rod which is attached to the steering linkage.

[0006] A worm and pinion type steering unit comprising a worm gear in toothed engagement with an output steering member, an input shaft receiving steering input from a steering wheel and having a lost motion connection to the worm gear, a fluid-actuated motor disposed adjacent the output end of the worm gear, open-center type valve means disposed between the output each of the worm gear and the fluid-actuated motor and operable to direct pressurized fluid from a fluid source to the fluid-actuated motor causing movement of a movable motor element, and means for translating the movement of this movable motor element into rotational movement of the worm gears, is known from US-A-4 060 146.

SUMMARY OF THE INVENTION

[0007] It is an object of the present invention to provide an improved torque generating steering device which may be utilized on vehicles having multiple hydraulic devices, but only a single pump, wherein the torque generator provides a load-pressure signal.

[0008] The above and other objects of the present invention are accomplished by the provision of a steering device adapted to receive a relatively low-torque input and translate this input into an output by means of a source of pressurized fluid having a fluid pressure responsive means for varying the fluid output of the fluid source; such steering device comprising housing means defining a fluid inlet port in fluid communication with said fluid source, and a fluid outlet port; fluid energy-translating displacement means, valve means disposed in the housing means and having a neutral position and an operating position in which the valve means and the housing means cooperate to define a fluid path communicating pressurized fluid from the inlet port to the displacement means, and from the displacement means to the outlet port; input shaft means operable to transmit the relatively low-torque input into movement of the valve means from the neutral position to the operating position; follow-up means operable to cause follow-up movement of the valve means from the operating position toward the neutral position, wherein the fluid path includes a main variable flow control orifice disposed in series flow relationship between the inlet port and the displacement means, the flow control orifice having a substantially zero flow area when the valve means is in the neutral position, and a maximum flow area when the valve means is in the operating position; whereby the housing means defines a load-sensing port adapted to be in fluid communication with the fluid pressure responsive means, the load-sensing port further being in fluid communication with the fluid path, downstream of the main variable flow control orifice; and wherein the valve means is configured to define a load sensing drain path to provide fluid communication between the load-sensing port and the fluid outlet port when the valve means is in the neutral position; characterized by:

(a) the steering device being a torque-generating steering device adapted to translate the relatively low-torque input into a relatively high-torque steering output;

(b) the fluid-energy-translating displacement means being associated with the housing means, and including a rotor member having relatively high-torque rotary motion in response to the flow of the pressurized fluid through the displacement means;

(c) the follow-up means being operable to transmit the rotary motion of the rotor member into the follow-up movement of the valve means from the operating position toward the neutral position;

(d) the steering device further comprising output shaft means operable to transmit the relatively high-torque rotary motion of the rotor member into the relatively high-torque steering output; and

(e) the load sensing drain path utilizing ports, slots and passages which are already included in the valve means to perform other functions.

BRIEF DESCRIPTION OF THE DRAWINGS

[0009] 

Fig. 1

is a somewhat schematic view of a hydraulic steering system including the torque-generating steering device of the present invention.

Fig. 2

is an axial cross-section through the torque-generating steering device shown in external plan view in Fig. 1.

Fig. 3

is a transverse cross-section taken on line 3-3 of Fig. 2, and on the same scale.

Figs. 4 and 5

are enlarged, plan views of the spool valve member and sleeve valve member, respectively, of the torque-generating steering device of the present invention.

Figs. 6 and 7

are enlarged, fragmentary layout views of the valving interface defined by the spool and sleeve valve members, illustrating the neutral and operating positions, respectively.

FIG. 8

is an orifice diagram, illustrating schematically the hydraulic circuit of the torque-generating steering device of the present invention.

DESCRIPTION OF THE PREFERRED EMBODIMENT

[0010] Referring now to the drawings, which are not intended to limit the invention, FIG. 1 illustrates somewhat schematically a hydraulic steering system including a torque-generating steering device, generally designated 11 and referred to hereinafter simply as a "torque generator". The torque generator 11 defines an inlet port 13 and an outlet port 15, which is connected to the system reservoir 17. The inlet port 13 is in fluid communication with the outlet port of a variable displacement hydraulic pump 19 which, by way of example only, may have a variable swashplate 21, the position of which determines the flow output of the pump 19, for any particular input speed. The position of the swashplate 21 is determined by a flow and pressure compensator, schematically designated as 23, which receives a load pressure signal 25 from the torque generator 11, as will be described in greater detail subsequently.

[0011] The torque generator 11 includes an input shaft 27 and an output shaft 29. Operably connected to the input shaft 27 is a steering wheel 31, whereby a relatively low-torque input is transmitted to the torque generator 11. As is well known to those skilled in the art, the primary function of the torque generator 11 is to receive the relatively low-torque input, and convert that input into a relatively high-torque steering output, which is transmitted by means of the output shaft 29 to any suitable device such as the pinion gear of a rack and pinion steering apparatus (not shown).

[0012] Referring now to FIG. 2, the torque generator 11 is comprised of a plurality of sections held in tight sealing engagement by a plurality of bolts 33, only one of which is shown in FIG. 2. The torque generator 11 comprises a valve housing section 35, having attached thereto, by means of a plurality of bolts 37, a front endcap 39, through which the input shaft 27 extends.

[0013] At the rearward end of the torque generator 11 (right end in FIG. 2) is a shaft support casing 41, through which the output shaft 29 extends. Disposed between the valve housing section 35 and the shaft support casing 41 is a gerotor displacement mechanism, generally designated 43, comprising an internally-toothed ring member 45 and an externally-toothed star member 47. As is well known to those skilled in the art, but by way of example only, the ring member 45 has a plurality N + 1 of internal teeth, and the star member 47 is eccentrically disposed within the ring member 45 and has a plurality N of external teeth. The star member 47 orbits and rotates within the ring member 45, and this relative orbital and rotational motion defines a plurality of expanding and contracting fluid volume chambers 49. In the subject embodiment, N is equal to 6, such that the ring member 45 has seven internal teeth, and the star member 47 has six external teeth, such that six orbits of the star within the ring results in one complete revolution of the star.

[0014] Referring still to FIG. 2, the valve housing section 35 defines the inlet port 13, as well as the outlet port 15 (not shown in FIG. 2). The housing section 35 defines a cylindrical valve bore 51. The housing section 35 further defines an annular groove 53, which is in fluid communication with the inlet port 13 by means of a passage 55. Similarly, the housing section 35 defines an annular groove 57, which is in open fluid communication with the outlet port 15 by means of a passage 59, shown only in dotted, fragmentary form in FIG. 2. Finally, the housing section 35 defines a plurality of meter passages 61 (see also FIG 3), each of which is disposed for fluid communication with one of the volume chambers 49.

[0015] Disposed between the gerotor 43 and the valve housing section 35 is a port plate 63, and disposed between the gerotor 43 and the shaft support casing 41 is another port plate 65. The port plate 63 defines a plurality of ports 67, each of which is disposed to permit fluid communication between one of the volume chambers 49 and its respective meter passage 61. In the subject embodiment, the port plate 65 defines a plurality of recesses 69 which may be substantially identical to the ports 67, to provide axial pressure balancing of the star member 47, as is well known to those skilled in the art.

[0016] Disposed within the valve bore 51 is a valve means, generally designated 71, comprising a primary, rotatable valve member 73 (spool valve), and a relatively rotatable, follow-up valve member 75 (sleeve valve). The spool valve 73 is preferably formed integral with the input shaft 27, for rotation therewith. Passing through the wall of the spool valve 73, and into engagement with the sleeve valve 75 is a plurality of spring members 77, the function of which is to bias the sleeve valve 75 toward a neutral position, relative to the spool valve 73, with the term "neutral" to be described in greater detail subsequently in connection with FIG. 6.

[0017] The gerotor displacement mechanism 43 has two primary functions in the torque generator 11. The first is to serve as a fluid meter, in response to the flow of pressurized fluid therethrough, and provide follow-up movement to the sleeve valve 75. In order to accomplish this follow-up function, the star member 47 is provided with a set of internal splines 79, and in engagement therewith is a set of crowned, external splines 81 formed about the rearward end of a driveshaft 83, the forward end of which is bifurcated and engages a pin member 85. The pin member 85 extends through oversized openings in the spool valve 73, in a manner well known in the art, and is received within openings in the sleeve valve 75, such that orbital and rotational motion of the star 47 is transmitted into follow-up rotation of the sleeve valve 75.

[0018] The other function of the gerotor mechanism 43 is to transmit a high-torque output to the output shaft 29. In order to accomplish this function, there is, in engagement with the internal splines 79 a set of crowned external splines 87 formed about one end of a main driveshaft 89 having, at its rearward end, another set of crowned external splines 91. The splines 91 are in engagement with a set of straight, internal splines 93 defined within the output shaft 29. Therefore, orbital and rotational movement of the star 47, in response to the flow of pressurized fluid through the gerotor 43, results in a relatively high-torque rotation of the output shaft 29.

[0019] Referring now to FIG. 5, the sleeve valve 75 defines a plurality of pressure ports 95, which are positioned axially to be in continuous fluid communication with the annular groove 53, and therefore, with the inlet port 13. The sleeve valve 75 also defines a plurality of return ports 97 which are in continuous fluid communication with the annular groove 57, and therefore, with the outlet port 15. Finally, the sleeve valve 75 defines a plurality of meter ports 99, each of which is disposed to be in commutating fluid communication with the opening of each of the meter passages 61 into the valve bore 51. In the subject embodiment, because there are seven (N + 1) of the volume chambers 49, and therefore seven of the meter passages 61, there are 12 (two times N) of the meter ports 99. Furthermore, by way of example only, there are eight of the pressure ports 95 and eight of the return ports 97. As may be seen in FIG. 5, as well as in FIGS. 6 and 7, the center of each of the pressure ports 95 and return ports 97 is circumferentially aligned with the center of one of the meter ports 99.

[0020] Referring now to FIG. 4, the spool valve 73 defines an annular groove 101, and in open communication therewith is a plurality of axial slots 103. Toward the forward end (left end in FIG. 4), the spool valve 73 defines another annular groove 105, and in open communication therewith, a plurality of axial slots 107.

[0021] It should be noted that the structure described thus far is generally well known in the torque generator art, except that in prior art torque generators which have all been open-center, the pressure ports 95 would be disposed further to the right in FIG. 5, in open communication with the annular groove 101, in much the same manner as the return ports 97 are in open communication with the annular groove 105. As was mentioned in the background of the present specification, it is an object of the present invention to provide a torque generator having the capability of providing the load-sensing signal 25 shown in FIG. 1 which may be utilized for varying the fluid output of the pump 19. In order for the torque generator of the present invention to provide a load-sensing signal, it is necessary for the valve means 71 to define a main, variable flow control orifice. Therefore, in accordance with one aspect of the present invention, the pressure ports 95 are disposed axially to the left (in FIGS. 4 and 5) of the annular groove 101, such that when the spool 73 and sleeve 75 are in their relative neutral position, fluid communication through the pressure ports 95 is blocked by the cylindrical, outer surface of the spool valve 73, i.e., the surface disposed between and around the interdigitated axial slots 103 and 107 (see FIG. 6).

[0022] Referring again to FIG. 5, the sleeve valve 75 defines an annular load-sensing groove 109 toward the right end of the sleeve. The sleeve 75 further defines a plurality of radial passages 111 which provide relatively unrestricted fluid communication between the annular groove 101 of the spool 73 and the load-sensing groove 109.

[0023] Referring now to FIG. 3, the valve housing section 35 defines an enlarged boss portion 113 which extends to the right in FIG. 3 and defines a load-sensing port 115. The housing section 35 further defines a radial passage 117 providing relatively unrestricted fluid communication between the load-sensing groove 109 and the load-sensing port 115.

Operation

[0024] Referring now primarily to FIGS. 7 and 8, the operation of the torque generator 11 of the present invention will be described. When the vehicle operator rotates the steering wheel 31 in a clockwise direction, the spool valve 73 is rotated clockwise, relative to the sleeve valve 75, from the neutral position shown in FIG. 6 to an operating position shown in FIG. 7, wherein the valve housing section 35, sleeve valve 75, and spool valve 73 cooperate to define a fluid path 119 (see FIG. 8) which flows from the inlet port 13 through the gerotor 43 to the outlet port 15.

[0025] When the spool valve 73 is rotated to the operating position, in response to a relatively low-torque input to the input shaft 27, half of the pressure ports 95 begin to communicate with the adjacent axial slots 103, the cumulative area of overlap of the pressure ports 95 and axial slots 103 providing a main variable flow control orifice 121. The pressurized fluid in the axial slot 103, downstream of the orifice 121, flows into the adjacent meter port 99, with the cumulative area of overlap of those meter ports 99 and the axial slots 103 providing a second variable flow control orifice 122. The fluid which flows through the orifice 122 is then communicated through successive meter passages 61 to the expanding volume chambers 49 of the gerotor 43. This flow of pressurized fluid to the expanding volume chambers causes orbital and rotational motion of the star 47, which is then transmitted by means of the main drive shaft 89 into a relatively high-torque steering output of the output shaft 29.

[0026] Fluid which is exhausted from the contracting volume chambers 49 of the gerotor 43 is communicated back through successive meter passages 61 to those meter ports 99 which are in communication with the axial slots 107. The cumulative overlap of these particular meter ports 99 and the axial slots 107 provides a third variable flow control orifice 123. After flowing through the orifice 123, the low-pressure exhaust fluid flows through the axial slot 107 into the annular groove 105, then flows through the return ports 97. The cumulative area of overlap of the groove 105 and the return ports 97 provides a relatively large, fixed orifice 124. As is well known to those skilled in the art, rotation of the steering wheel 31 at a relatively constant speed and torque will achieve a certain displacement of the spool valve 73, relative to the sleeve valve 75 (such as that shown in FIG. 7), and the flow through the gerotor 43, and resulting follow-up movement transmitted to the sleeve 75 by means of the drive shaft 83 and pin 85, will maintain the relative displacement of the spool and sleeve.

[0027] With the spool valve 73 and sleeve valve 75 in the operating position illustrated in FIG. 7, the pressurized fluid in the axial slots 103 is representative of the steering load, i.e., the torque on the output shaft 29. The load pressure in the axial slots 103 is also present in the annular groove 101, and is communicated through the radial passages 111 into the load-sensing groove 109. The load pressure is then communicated through the radial passage 117 to the load-sensing port 115, from where it is communicated back to the compensator 23 of the pump 19 as described previously.

[0028] As is well known to those skilled in the general art of load-sensing valving, it is necessary to provide a fluid path to drain the entire load signal circuit whenever the valve returns to its neutral position, from an operating position. Draining the load signal circuit permits the pump to destroke to a relatively low-pressure, standby condition, thus minimizing the horsepower required to drive the pump. One important aspect of the present invention is to provide a drain path for the load-sensing circuit which is relatively simple, does not add to the overall size of the spool and sleeve valves, and utilizes only ports, slots, and passages which are already included in the valving, to perform other functions. Referring to FIG. 6, when the spool and sleeve are again in the neutral position, the load pressure fluid throughout the load-sensing circuit, described previously, is communicated through each of the axial slots 103 into each of the overlapping pressure ports 99. With each of the pressure ports 99 being large enough to communicate with both the axial slot 103 and the axial slot 107, the load pressure fluid flows into each of the slots 107, then into the annular groove 105. From the groove 105, the load pressure fluid flows through the return ports 97, and then to the outlet port 15, in the same manner as in the normal fluid path 119 when the spool and sleeve are in the operating position.

[0029] It will be understood by those skilled in the art that the load pressure signal 25 provided by the present invention may be utilized in ways other than to control the swash angle of a variable displacement pump, as shown in FIG. 1. The load signal 25 could be communicated to a load-sensing priority flow control valve in circuits of the type illustrated and described in U.S. Patent No. 4,043,419, assigned to the assignee of the present invention, and incorporated herein by reference. As another example, the load signal 25 could be sensed, such as by means of a pressure transducer, with the resulting electrical pressure signal being utilized in a control circuit, such as to control the speed of operation of an electric motor used to drive the hydraulic pump, serving as the source of fluid to the torque generator.

[0030] The invention has been described in great detail, sufficient to enable one skilled in the art to make and use the same. Various alterations and modifications of the invention will occur to those skilled in the art upon a reading and understanding of the foregoing specification, and it is intended to include all such alterations and modifications as part of the invention, insofar as they come within the scope of the appended claims.

Claims

1. A steering device adapted to receive a relatively low-torque input and translate said input into an output by means of a source (19) of pressurized fluid having a fluid pressure responsive means (23) for varying the fluid output of said fluid source; said steering device comprising housing means (35) defining a fluid inlet port (13) in fluid communication with said fluid source, and a fluid outlet port (15); fluid energy-translating displacement means (43); valve means (71) disposed in said housing means and having a neutral position and an operating position in which said valve means and said housing means cooperate to define a fluid path (119) communicating pressurized fluid from said inlet port (13) to said displacement means (43), and from said displacement means to said outlet port (15); input shaft means (27) operable to transmit said relatively low-torque input into movement of said valve means from said neutral position to said operating position; follow-up means (83, 85) operable to cause follow-up movement of said valve means from said operating position toward said neutral position, wherein said fluid path includes a main variable flow control orifice (121) disposed in series flow relationship between the inlet port (13) and the displacement means (43), said flow control orifice having a substantially zero flow area when said valve means is in said neutral position, and a maximum flow area when said valve means is in said operating position; whereby said housing means defines a load-sensing port (115) adapted to be in fluid communication with said fluid pressure responsive means (23), said load-sensing port further being in fluid communication with said fluid path, downstream of said main variable flow control office (121); and wherein said valve means is configured to define a load sensing drain path (101, 103, 99, 107, 105, 97, 15) to provide fluid communication between said load-sensing port (115) and said fluid outlet port (15) when said valve means is in said neutral position; characterized by:

(a) said steering device being a torque-generating steering device (11) adapted to translate said relatively low-torque input into a relatively high-torque steering output;

(b) said fluid-energy-translating displacement means (43) being associated with said housing means (35), and including a rotor member (47) having relatively high-torque rotary motion in response to the flow of said pressurized fluid through said displacement means (43);

(c) said follow-up means (83, 85) being operable to transmit said rotary motion of said rotor member (47) into said follow-up movement of said valve means (71) from said operating position toward said neutral position;

(d) said steering device further comprising output shaft means (29) operable to transmit said relatively high-torque rotary motion of said rotor member (47) into said relatively high-torque steering output; and

(e) said load sensing drain path (101, 103, 99, 107, 105, 97, 15) utilizing ports, slots and passages which are already included in said valve means (71) to perform other functions.

2. A torque-generating steering device as claimed in claim 1 characterized by said valve means comprising a primary, rotatable valve member (73), and a relatively rotatable follow-up valve member (75), said primary valve member being fixed to rotate with said input shaft means, and said follow-up valve member receiving said follow-up movement.

3. A torque-generating steering device as claimed in claim 2 characterized by said primary valve member (73) comprising a generally cylindrical spool valve member, and said follow-up valve member (75) comprising a generally cylindrical sleeve valve member disposed radially between said spool valve member and said housing means.

4. A torque-generating steering device as claimed in claim 3 characterized by said housing means defining a plurality of meter passages (61) providing fluid communication between said valve means and said displacement means, said housing means defining a generally cylindrical valve bore (51) adapted to receive said sleeve valve member therein, said plurality of meter passages being in open communication with said valve bore at a plurality of circumferentially disposed locations.

5. A torque-generating steering device as claimed in claim 4 characterized by said sleeve valve member (75) defining a plurality of meter ports (99), disposed to be in commutating fluid communication with said plurality of meter passages in response to rotation of said sleeve valve member.

6. A torque-generating steering device as claimed in claim 5 characterized by said sleeve valve member (75) defining a plurality of pressure ports (95) disposed toward one axial end of said sleeve valve member, from said meter ports, and further defining a plurality of return ports (97), disposed toward the other axial end of said sleeve valve member, from said meter ports.

7. A torque-generating steering device as claimed in claim 6 characterized by said pressure ports (95) being in open, continuous fluid communication with said inlet port (13), and said return ports (97) being in open, continuous fluid communication with said outlet port (15).

8. A torque-generating steering device as claimed in claim 7 characterized by said spool valve member defining a first plurality of axial slots (103), each of said first axial slots being disposed to provide fluid communication from one of said pressure ports (95) to one of said meter ports (99) when said valve means is in said operating position.

9. A torque-generating steering device as claimed in claim 8 characterized by said spool valve member defining a second plurality of axial slots (107), each of said second axial slots being disposed to provide fluid communication from one of said meter ports (99) to one of said return ports (97) when said valve means is in said operating position.

10. A torque-generating steering device as claimed in claim 8 characterized by said first axial slots (103) and said pressure ports (95) cooperating to define said main variable flow control orifice (121).

11. A torque-generating steering device as claimed in claim 10 characterized by said spool valve member (73) defining a pressure annular groove (101) in open fluid communication with said first axial slots (103), downstream of said first variable flow control orifice (121), and said sleeve valve member (75) and said housing means (35) cooperating to define an annular groove (109) in open fluid communication with said load-sensing port (115), said sleeve valve member further defining passage means (111) providing fluid communication between said spool annular groove (101) and said sleeve annular groove (109).

12. A torque-generating steering device as claimed in claim 11 characterized by said first axial slots (103) and said meter ports (99) cooperating to define a second variable flow control orifice (122), and said second axial slots (107) and said meter ports (99) cooperating to define a third variable flow control orifice (123).

13. A torque-generating steering device as claimed in claim 12 characterized by at least one of said meter ports (99) being in open fluid communication with one of said first axial slots (103), and with one of said second axial slots (107), simultaneously, when said valve means is in said neutral position, thereby providing fluid communication between said load-sensing port (115) and said outlet port (15) when said valve means is in said neutral position.

Ansprüche

1. Lenkeinrichtung, die eine einem relativ kleinen Drehmoment entsprechende Eingangsgröße aufnehmen und diese in eine Ausgangsgröße mittels einer Quelle (19) für unter Druck stehendes Fluid umsetzen kann, die eine auf Fluiddruck ansprechende Anordnung (23) zum Variieren der Fluidausgangsgröße der Fluidquelle aufweist; wobei die Lenkeinrichtung versehen ist mit einer Gehäuseanordnung (35), die einen mit der Fluidquelle in Fluidverbindung stehenden Fluideinlaß (13) und einen Fluidauslaß (15) aufweist; mit einer Fluidenergie umsetzenden Verdrängungsvorrichtung (43); einer in der Gehäuseanordnung untergebrachten Ventilanordnung (71), die eine Neutralstellung und eine Arbeitsstellung aufweist, in welcher die Ventilanordnung und die Gehäuseanordnung gemeinsam einen Fluidweg (119) bilden, der unter Druck stehendes Fluid von dem Einlaß (13) zu der Verdrängungsvorrichtung (43) und von der Verdrängungsvorrichtung zu dem Auslaß (15) gelangen läßt; einer Antriebswellenanordnung (27) zum Umsetzen der einem relativ kleinen Drehmoment entsprechenden Eingangsgröße in eine Bewegung der Ventilanordnung von der Neutralstellung zu der Arbeitsstellung; einer Nachlaufanordnung (83, 85), mittels deren für eine Nachlaufbewegung der Ventilanordnung von der Arbeitsstellung in Richtung auf die Neutralstellung gesorgt werden kann, wobei der Fluidweg eine verstellbare Hauptdurchflußsteueröffnung (121) aufweist, die strömungsmäßig in Reihe zwischen dem Einlaß (13) und der Verdrängungsvorrichtung (43) liegt und die einen Durchflußquerschnitt von im wesentlichen Null hat, wenn sich die Ventilanordnung in der Neutralstellung befindet, und die einen maximalen Durchflußquerschnitt hat, wenn sich die Ventilanordnung in der Arbeitsstellung befindet; wobei die Gehäuseanordnung einen Lasterfassungsanschluß (115) bildet, der in Fluidverbindung mit der auf Fluiddruck ansprechenden Anordnung (23) stehen kann und der mit dem Fluidweg stromab von der verstellbaren Hauptdurchflußsteueröffnung (121) in Fluidverbindung steht; und wobei die Ventilanordnung zur Bildung eines Lasterfassungs-Ablaufweges (101, 103, 99, 107, 105, 97, 15) ausgelegt ist, um für eine Fluidverbindung zwischen dem Lasterfassungsanschluß (115) und dem Fluidauslaß (15) zu sorgen, wenn sich die Ventilanordnung in der Neutralstellung befindet, dadurch gekennzeichnet, daß:

(A) die Lenkeinrichtung eine Drehmoment erzeugende Lenkeinrichtung (11) ist, die die einem relativ kleinen Drehmoment entsprechende Eingangsgröße in eine einem relativ großen Drehmoment entsprechende Lenkausgangsgröße umsetzen kann;

(B) die Fluidenergie umsetzende Verdrängungsvorrichtung (43) der Gehäuseanordnung (35) zugeordnet ist und ein Rotorbauteil (47) aufweist, das auf den Durchfluß des unter Druck stehenden Fluids durch die Verdrängungsvorrichtung (43) hin eine Drehbewegung mit relativ großem Drehmoment ausführt;

(C) mittels der Nachlaufanordnung (83, 85) diese Drehbewegung des Rotorbauteils (47) in die Nachlaufbewegung der Ventilanordnung (71) von der Arbeitsstellung in Richtung auf die Neutralstellung umsetzbar ist;

(D) die Lenkeinrichtung ferner eine Abtriebswellenanordnung (29) aufweist, mittels deren die Drehbewegung des Rotorbauteils (47) mit relativ großem Drehmoment in die Lenkausgangsgröße mit relativ großem Drehmoment umsetzbar ist; und

(E) der Lasterfassungs-Ablaufweg (101, 103, 99, 107, 105, 97, 15) Anschlüsse, Schlitze und Durchlässe nutzt, die in der Ventilanordnung (71) bereits zur Durchführung anderer Funktionen vorhanden sind.

2. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Ventilanordnung ein drehbares Hauptventilorgan (73) und ein relativ drehbares Nachlautventilorgan (75) aufweist, wobei das Hauptventilorgan mit der Antriebswellenanordnung drehfest verbunden ist und das Nachlautventilorgan zu der Nachlaufbewegung veranlaßt wird.

3. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 2, dadurch gekennzeichnet, daß das Hauptventilorgan (73) ein im wesentlichen zylindrisches Spulenventilorgan aufweist und das Nachlautventilorgan (75) ein im wesentlichen zylindrisches Hülsenventilorgan aufweist, das radial zwischen dem Spulenventilorgan und der Gehäuseanordnung angeordnet ist.

4. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 3, dadurch gekennzeichnet, daß die Gehäuseanordnung eine Mehrzahl von Dosierdurchlässen (61) bildet, die für eine Fluidverbindung zwischen der Ventilanordnung und der Verdrängungsvorrichtung sorgen, wobei die Gehäuseanordnung mit einer im wesentlichen zylindrischen Ventilbohrung (51) versehen ist, die zur Aufnahme des Hülsenventilorgans geeignet ist und wobei die Mehrzahl von Dosierdurchlässen mit der Ventilbohrung an einer Mehrzahl von in Umfangsrichtung verteilt angeordneten Stellen in offener Verbindung stehen.

5. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 4, dadurch gekennzeichnet, daß das Hülsenventilorgan (75) eine Mehrzahl von Dosieröffnungen (99) bildet, die in Abhängigkeit von einer Drehbewegung des Hülsenventilorgans mit der Mehrzahl von Dosierdurchlässen in kommutierende Fluidverbindung kommen.

6. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 5, dadurch gekennzeichnet, daß das Hülsenventilorgan (75) eine Mehrzahl von Drucköffnungen (95) bildet, die von den Dosieröffnungen aus gesehen in Richtung auf das eine axiale Ende des Hülsenventilorgans angeordnet sind, und daß das Hülsenventilorgan eine Mehrzahl von Rücklauföffnungen (97) bildet, die von den Dosieröffnungen aus gesehen in Richtung auf das andere axiale Ende des Hülsenventilorgans angeordnet sind.

7. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 6, dadurch gekennzeichnet, daß die Drucköffnungen (95) mit dem Einlaß (13) in offener, ständiger Fluidverbindung stehen, und daß die Rücklauföffnungen (97) mit dem Auslaß (15) in offener, ständiger Fluidverbindung stehen.

8. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 7, dadurch gekennzeichnet, daß das Spulenventilorgan eine erste Mehrzahl von Axialschlitzen (103) bildet, von denen jeder so angeordnet ist, daß er für eine Fluidverbindung von einer der Drucköffnungen (95) zu einer der Dosieröffnungen (99) sorgt, wenn sich die Ventilanordnung in der Arbeitsstellung befindet.

9. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 8, dadurch gekennzeichnet, daß das Spulenventilorgan eine zweite Mehrzahl von Axialschlitzen (107) bildet, von denen jeder so angeordnet ist, daß er für eine Fluidverbindung von einer der Dosieröffnungen (99) zu einer der Rücklauföffnungen (97) sorgt, wenn sich die Ventilanordnung in der Arbeitsstellung befindet.

10. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 8, dadurch gekennzeichnet, daß die ersten Axialschlitze (103) und die Drucköffnungen (95) zusammen die verstellbare Hauptdurchflußsteueröffnung (121) bilden.

11. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 10, dadurch gekennzeichnet, daß das Spulenventilorgan (73) eine Druckringnut (101) bildet, die mit den ersten Axialschlitzen (103) stromab von der ersten verstellbaren Durchflußsteueröffnung (121) in offener Fluidverbindung steht, und daß das Hülsenventilorgan (75) und die Gehäuseanordnung (35) zusammen eine mit dem Lasterfassungsanschluß (115) in offener Fluidverbindung stehende Ringnut (109) bilden, wobei das Hülsenventilorgan ferner eine Durchlaßanordnung (111) bildet, die für eine Fluidverbindung zwischen der Ringnut (101) des Spulenventilorgans und der Ringnut (109) des Hülsenventilorgans sorgt.

12. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 11, dadurch gekennzeichnet, daß die ersten Axialschlitze (103) und die Dosieröffnungen (99) zusammen eine zweite verstellbare Durchflußsteueröffnung (122) bilden, und daß die zweiten Axialschlitze (107) und die Dosieröffnungen (99) zusammen eine dritte verstellbare Durchflußsteueröffnung (123) bilden.

13. Drehmoment erzeugende Lenkeinrichtung nach Anspruch 12, dadurch gekennzeichnet, daß bei in der Neutralstellung befindlicher Ventilanordnung mindestens eine der Dosieröffnungen (99) mit einem der ersten Axialschlitze (103) und gleichzeitig mit einem der zweiten Axialschlitze (107) in offener Fluidverbindung steht, wodurch für eine Fluidverbindung zwischen dem Lasterfassungsanschluß (115) und dem Auslaß (15) gesorgt wird, wenn die Ventilanordnung in der Neutralstellung steht.

Revendications

1. Dispositif de direction apte à recevoir un signal d'entrée de couple relativement faible et à convertir ledit signal d'entrée en un signal de sortie au moyen d'une source (19) de fluide sous pression comportant des moyens (23) sensibles à la pression du fluide pour modifier le signal de sortie du fluide de ladite source de fluide; ledit dispositif de direction comprenant des moyens formant carter (35) définissant un orifice d'entrée du fluide (13) en communication fluidique avec ladite source de fluide, et un orifice de sortie du fluide (15); des moyens de déplacement (43) convertissant l'énergie du fluide; des moyens formant soupape (71) disposés dans lesdits moyens formant carter et possédant une position neutre et une position de fonctionnement, dans laquelle lesdits moyens formant soupape et lesdits moyens formant carter coopèrent pour définir un trajet (119) pour le fluide, qui transfère le fluide sous pression dudit orifice d'entrée (13) auxdits moyens de déplacement (43) et qui s'étend depuis lesdits moyens de déplacement jusqu'audit orifice de sortie (15); des moyens formant arbre d'entrée (27) aptes à fonctionner de manière à convertir ledit signal d'entrée de couple relativement faible en un déplacement desdits moyens formant soupape depuis ladite position neutre jusqu'à ladite position de fonctionnement; des moyens de suivi (83,85) pouvant fonctionner de manière à provoquer un déplacement de suivi desdits moyens formant soupape depuis ladite position de fonctionnement en direction de ladite position neutre, ledit trajet du fluide comprenant un orifice de commande principal à écoulement variable (121) disposé selon une disposition fluidiquement en série entre l'orifice d'entrée (13) et les moyens de déplacement (43), ledit orifice de commande d'écoulement possédant une surface d'écoulement sensiblement nulle lorsque lesdits moyens formant soupape sont dans ladite position neutre, et une surface d'écoulement maximale lorsque lesdits moyens formant soupape sont dans ladite position de fonctionnement; lesdits moyens formant carter définissant l'orifice de détection de charge (115) apte à être placé en communication fluidique avec lesdits moyens (23) répondant à la pression du fluide, ledit orifice de détection de charge étant en outre en communication fluidique avec ledit trajet pour le fluide, en aval dudit orifice principal de commande d'écoulement variable (121); et lesdits moyens formant soupape étant agencés de manière à définir un trajet d'évacuation et de détection de charge (101,103,99,107,105,97,15) pour établir une communication fluidique entre ledit orifice de détection de charge (115) et ledit orifice de sortie de fluide (15), lorsque lesdits moyens formant soupape sont dans ladite position neutre; caractérisé en ce que :

(a) ledit dispositif de direction est un dispositif de direction (11) produisant un couple et qui est adapté pour convertir ledit signal d'entrée de couple relativement faible en un signal de sortie de braquage à couple relativement élevé;

(b) lesdits moyens de déplacement (43) réalisant une conversion de l'énergie fluidique étant associés auxdits moyens formant carter (35) et comprenant un élément de rotor (47) qui se déplace selon un mouvement de rotation à couple relativement élevé pour faire circuler ledit fluide sous pression dans lesdits moyens de déplacement (43);

(c) lesdits moyens de suivi (83,85) pouvant agir de manière à convertir ledit mouvement de rotation dudit élément formant rotor (47) dans ledit déplacement de suivi desdits moyens formant soupape (71) depuis ladite position de fonctionnement en direction de ladite position neutre;

(d) ledit dispositif de direction comporte en outre des moyens formant arbre de sortie (29) pouvant agir de manière à convertir ledit mouvement de rotation à couple relativement intense dudit élément formant rotor (47) en ledit signal de sortie de braquage à couple relativement élevé; et

(e) ledit trajet d'évacuation et de détection de charge (101,103,99,107,105,97,15) utilise des orifices, des fentes et des passages qui sont déjà présents dans lesdits moyens formant soupape (71) pour assumer d'autres fonctions.

2. Dispositif de direction produisant un couple selon la revendication 1, caractérisé par des moyens formant soupape comprenant un élément de soupape rotatif primaire (63) et un élément de soupape de suivi (75), aptes à tourner de façon relative, ledit élément de soupape primaire étant fixé auxdits moyens formant arbre d'entrée pour tourner avec ces derniers, et ledit élément de soupape de suivi exécutant ledit déplacement de suivi.

3. Dispositif de direction produisant un couple selon la revendication 2, caractérisé en ce que ledit élément de soupape primaire (73) comprend un élément de soupape en forme de tiroir essentiellement cylindrique, et ledit élément de soupape de suivi (75) comprend un élément de soupape en forme de manchon essentiellement cylindrique disposé radialement entre ledit élément de soupape à tiroir et lesdits moyens formant carter.

4. Dispositif de direction produisant un couple selon la revendication 3, caractérisé en ce que lesdits moyens formant carter définissent une pluralité de passages de dosage (61) établissant une communication fluidique entre lesdits moyens formant soupape et lesdits moyens de déplacement, lesdits moyens formant carter définissant un perçage de soupape essentiellement cylindrique (51) apte à loger ledit élément de soupape en forme de manchon, ladite pluralité de passages de dosage étant en communication libre avec ledit perçage de soupape en une pluralité d'emplacements disposés circonférentiellement.

5. Dispositif de direction produisant un couple selon la revendication 4, caractérisé en ce que ledit élément de soupape en forme de manchon (75) définit une pluralité d'orifices de dosage (99), disposés de manière à établir une communication fluidique à commutation avec ladite pluralité de passages de dosage en réponse à une rotation dudit élément de soupape en forme de manchon.

6. Dispositif de direction produisant un couple selon la revendication 5, caractérisé en ce que ledit élément de soupape en forme de manchon (75) définit une pluralité d'orifices de pression (95) disposés en direction d'une extrémité axiale dudit élément de soupape en forme de manchon, à partir desdits orifices de dosage, et définit en outre une pluralité d'orifices de retour (97) disposés en direction de l'autre extrémité axiale dudit élément de soupape en forme de manchon, à partir desdits orifices de dosage.

7. Dispositif de direction produisant un couple selon la revendication 6, caractérisé en ce que lesdits orifices de pression (95) sont reliés selon une communication fluidique continue ouverte avec ledit orifice d'entrée (13), et que lesdits orifices de retour (97) sont reliés selon une communication fluidique continue et ouverte audit orifice de sortie (15).

8. Dispositif de direction produisant un couple selon la revendication 7, caractérisé en ce que ledit élément de soupape en forme de tiroir définit une première pluralité de fentes axiales (103), chacune desdites premières fentes axiales étant disposée de manière à établir une communication fluidique depuis l'un desdits orifices de pression (95) en direction de l'un desdits orifices de dosage (99) lorsque lesdits moyens formant soupape sont dans ladite position de fonctionnement.

9. Dispositif de direction produisant un couple selon la revendication 8, caractérisé en ce que ledit élément de soupape en forme de tiroir définit une seconde pluralité de fentes axiales (107), chacune desdites secondes fentes axiales étant disposée de manière à établir une communication fluidique entre l'un desdits orifices de dosage (99) et l'un desdits orifices de retour (97) lorsque lesdits moyens formant soupape sont dans ladite position de fonctionnement.

10. Système de direction produisant un couple selon la revendication 8, caractérisé en ce que lesdites premières fentes axiales (103) et lesdits orifices de pression (95) coopèrent pour définir ledit orifice principal de commande d'écoulement variable (121).

11. Dispositif de direction produisant un couple selon la revendication 10, caractérisé en ce que ledit élément de soupape en forme de tiroir (73) définit une gorge annulaire de pression (101) en communication fluidique ouverte avec lesdites premières fentes axiales (33), en aval dudit premier orifice de commande d'écoulement variable (121), et ledit élément de soupape en forme de manchon (75) et lesdits moyens formant carter (35) coopèrent pour définir une gorge annulaire (109) en communication fluidique ouverte avec ledit orifice de détection de charge (115), ledit élément de soupape en forme de manchon définissant en outre des moyens en forme de passages (111) établissant une communication fluidique entre ladite gorge annulaire (101) dudit tiroir et ladite gorge annulaire (109) du manchon.

12. Dispositif de direction produisant un couple selon la revendication 11, caractérisé en ce que lesdites premières fentes axiales (103) et lesdits orifices de dosage (99) coopèrent pour définir un second orifice de commande d'écoulement variable (122), et lesdites secondes fentes axiales (107) et lesdits orifices de dosage (99) coopèrent pour définir un troisième orifice de commande d'écoulement variable (123).

13. Dispositif de direction produisant un couple selon la revendication 12, caractérisé en ce qu'au moins l'un desdits orifices de dosage (99) est en communication fluidique ouverte avec l'une desdites premières fentes axiales (103), et simultanément avec l'une desdites secondes fentes axiales (107), lorsque lesdits moyens formant soupape sont dans ladite position neutre, ce qui établit une communication fluidique entre ledit orifice de détection de charge (115) et ledit orifice de sortie (15) lorsque lesdits moyens formant soupape sont dans ladite position neutre.

Drawing